Method and apparatus for improved roll static angle adjustment

ABSTRACT

The present invention relates to a method and apparatus for providing improved roll static angle adjustment for head gimbal assemblies (HGA&#39;s) used in disc drives. In the method, proximal and distal clamping members are attached to a load beam of the HGA and are separated by a distance of 4-30% of the length of the load beam. One of the distal and proximal clamping members is rotated about a longitudinal axis of the load beam such that the relative angular position of the distal and proximal clamping members reaches an adjust angle. Also disclosed is a rigid beam section of an HGA that includes apertures which are positioned along maximum stress contours where early plastic deformation of the rigid beam section is desired during adjustment of the roll static angle.

CROSS-REFERENCE TO RELATED APPLICATION

This is a Divisional Application No. 09/730,052, filed Dec. 5, 2000, nowU.S. Pat. No. 6,366,430, B1, which claims priority of U.S. ProvisionalApplication No. 60/169,204, filed Dec. 6, 1999 by Shri Han Narayan, PaulE. Kupinski and Sandeepan Bhattacharya for “IMPROVED RSA ADJUSTMETHODOLOGY AND RELATED SUSPENSION DESIGNS; this application is also acontinuation of International Application No. PCT/US00/42550, filed onan even date herewith for “Method and Apparatus for Improved Roll StaticAngle Adjustment,” which in turn claims priority of the aforementionedU.S. Provisional Application.

FIELD OF THE INVENTION

The present invention relates to disc storage systems. Morespecifically, the present invention relates to a method and apparatusfor adjusting the roll static angle of a disc drive suspension.

BACKGROUND OF THE INVENTION

Disc drives of the “Winchester” type are well known in the industry.Such drives use rigid discs coated with a magnetizable medium forstorage of digital information in a plurality of circular, concentricdata tracks. The discs are mounted on a spindle motor which causes thediscs to spin and the surfaces of the discs to pass under respectiverecording heads. Each head includes a hydrodynamic (e.g. air) bearingslider and a transducer for writing information to and readinginformation from the disc surface. An actuator mechanism moves the headsfrom track to track across the surfaces of the discs under control ofelectronic circuitry. The actuator mechanism includes a track accessingarm and a head gimbal assembly (HGA) for each head.

The HGA generally includes a load beam and a gimbal. The load beamincludes a rigid beam section to which the gimbal is attached. The rigidbeam section of the load beam transfers a pre-load force from a flexiblebeam portion to the head which forces the head toward the disc surface.The gimbal is positioned between the rigid beam section of the load beamand the slider to provide a resilient connection that allows the sliderto pitch and roll while following the typography of the disc.

One important performance-related criteria of the HGA is known as itsstatic attitude. The static attitude of the slider refers to thepositional orientation of the slider with respect to the surface of thedisc over which it is flying. The slider is generally designed to fly ata predetermined orientation (typically parallel) with the surface of thedisc. Deviations from this parallel relationship which result in thefront and back edges of the slider being at different heights from thedisc are known as pitch errors. Deviations from this parallelrelationship which result in the opposite sides of the slider being atdifferent heights from the disc are known as roll errors. Any pitch orroll error in the desired flying attitude of the slider can degrade theperformance of the disc drive. As a result, it is preferable to zero thepitch and roll angles of the head when mounted to the HGA.

The load beam, as with all mechanical structures, has a resonantfrequency, which can cause instability in the HGA. The first bendingmode of the HGA generally causes the load beam to vibrate or move in avertical plane or a plane that is transverse to the plane of the loadbeam when the load beam is symmetric about a longitudinal axis of theload beam. However, when a twist is made in the rigid beam section ofthe load beam about the longitudinal axis, the load beam becomesasymmetric about the longitudinal axis. As a result, the load beam willalso vibrate or oscillate in a horizontal plane at the resonantfrequency. This horizontal movement produces off-track errors therebylimiting the performance of the disc drive.

When the head is mounted to the load beam, it is generally oriented withnon-zero roll and pitch angles. The roll and pitch angles can be forcedto zero degrees using a static attitude adjust machine (SAAM). Clampingmembers of the SAAM attach to the rigid beam section and twist the rigidbeam section along its longitudinal axis to set the roll static angle ofthe head to zero degrees. Prior art methods have positioned the clampingmembers at the extreme ends of the rigid beam section to maximize thedistance separating them. The desire was to minimize the amount of twistper unit length of the rigid beam section to avoid damaging the rigidbeam section. Unfortunately, these prior art methods produce HGA'shaving undesirable off-track errors.

There remains a continuing need for improved methods for adjusting theroll static attitude of the load beam. In particular, there is need toimprove the sensitivity of the load beam twisting by the SAAM whilesimultaneously reducing off-track errors resulting from the firstbending mode of the HGA.

SUMMARY OF THE INVENTION

The present invention relates to a method and apparatus for providingimproved roll static angle adjustment for head gimbal assemblies (HGA's)used in a disc drive. The method of the present invention improves rollstatic angle adjustment of a head located at a distal end of an HGA. Inthe method, a high stress region is formed in the rigid beam sectionproximate a distal end where a distal clamping member is coupled. Aproximal clamping member is coupled to the rigid beam section a distanceaway from the distal clamping member. Finally at least one of the distaland proximal clamping members is rotated about the longitudinal axissuch that a relative angular position of the distal and proximalclamping members reaches an adjust angle resulting in a change in theroll static angle of the head.

The apparatus of the present invention is directed to a load beam of anHGA for use in a disc drive. The load beam includes a mounting portion,a flexure arm, and a rigid beam section. The mounting portion is adaptedto couple the load beam to a track accessing arm of the disc drive. Theflexible beam portion is attached to the mounting portion and is adaptedto supply a pre-load force to a head of the HGA through the flexure arm.The rigid beam section includes a proximal end that is attached to themounting portion, a distal end attached to the flexure arm, and a highstress region. The high stress region includes a plurality of apertureswhich define high stress contours of the rigid beam section whereplastic deformation is desired during roll static angle adjustment.

These and various other features as well as advantages whichcharacterize the present invention will be apparent upon reading of thefollowing detailed description and review of the associated drawings.

BRIEF DESCRIPTION OF THE DRAWINGS

FIG. 1 is a perspective view of a disc drive in accordance with oneembodiment of the present invention.

FIG. 2 shows a perspective view of a head gimbal assembly in accordancewith one embodiment of the invention.

FIG. 3 shows a cross-sectional view of view of a head gimbal assembly inaccordance with one embodiment of the invention, taken at line 3—3 ofFIG. 2.

FIG. 4 shows a simplified top plan view of a head gimbal assembly withclamping members of a static attitude adjust machine positioned along arigid beam portion in accordance with one embodiment of the presentinvention.

FIG. 5 shows a magnified view of the portion of the head gimbal assemblyof FIG. 4 that is contained in circle 4.

FIG. 6 is a flowchart representing a method of adjusting the low staticangle of a head of a head gimbal assembly, in accordance with oneembodiment of the invention.

DETAILED DESCRIPTION OF ILLUSTRATIVE EMBODIMENTS

FIG. 1 is a perspective view of a disc drive 110 in which benefits ofthe present invention can be realized. Disc drive 110 includes a housingwith a base 112 and a top cover (not shown). Disc drive 110 furtherincludes a disc pack L14, which is mounted on a spindle motor (notshown) by a disc clamp 116. Disc pack 114 includes a plurality ofindividual discs which are mounted for co-rotation about central axis118. Each disc surface has an associated head 120 which is mounted todisc drive 110 for communication with the disc surface. In the exampleshown, heads 120 are supported by head gimbal assemblies (HGA's) 122which are in turn attached to track accessing arms 124 of actuator 126.Actuator 126 is of the type known as a rotary moving coil actuator andincludes a voice coil motor, shown generally at 128. Voice coil motor128 rotates actuator 126 with its attached heads 120 about a pivot shaft130 to position heads 120 over a desired data track along a path 132between a disc inner diameter 134 and a disc outer diameter 136. Voicecoil motor operates under control of internal circuitry 138. Writecircuitry within internal circuitry 138 encodes the data to be storedinto successive code words and sends the code words in the form of aserial analog write signal to the write transducer on head 120 whichencodes magnetic flux reversals within a magnetic layer on the discsurface.

FIG. 2 shows a perspective view of an example of HGA 122 and FIG. 3shows a cross-sectional view of head 120, taken at line 3—3 of FIG. 2,mounted to HGA 122 and positioned above disc surface 140. Also shown inFIGS. 2 and 3 are x-axis 142, y-axis 144, and z-axis 146. Typical HGA's122 include load beam 148 and gimbal 150. Load beam 148 generallyincludes mounting portion 152, flexible beam portion 154, rigid beamsection 156, longitudinal axis 158 aligned with x-axis 142, and flexurearm 160. Mounting portion 152 includes swage hole 162 which mounts totrack accessing arm 124 (shown in FIG. 1) through a base plate (notshown). Flexible beam portion 154 applies a pre-load force to head 120through rigid beam section 156 and flexure arm 160 to limit the flyingheight of head 120. The pre-load force can be applied to head 120 atdimple 164 of flexure arm 160.

Each head 120 includes a hydrodynamic (e.g. air) bearing slider 166 anda transducer (not shown) for writing information to, and readinginformation from, disc surface 140. Gimbal 150 is positioned betweenrigid beam section 156 of load beam 148 and slider 166 to provide aresilient connection that allows slider 166 to pitch (rotate about thez-axis 146) and roll (rotate about longitudinal axis 158 or the x-axis142) while following the typography of disc surface 140. Slider 166includes air-bearing surfaces 168 which face disc surface, 140. Forexample, a conventional catamaran slider includes an air-bearing surface168 that includes a pair of raised side rails 170 and 172 which facedisc surface 140, as shown in FIG. 2. Air-bearing surfaces 170 and 172are aligned approximately parallel to the tangential velocity of thedisc. As disc 140 rotates, air passes beneath air-bearing surfaces 168and skin friction on air bearing surfaces 168 causes the air pressurebetween the surface of disc 140 and air-bearing surfaces 168 to increasewhich creates a hydrodynamic lifting force that causes slider 166 flyabove the surface of disc 140. The pre-load force and the hydrodynamiclifting force reach an equilibrium based upon the hydrodynamicproperties of the slider and the speed of rotation of disc 140.

It is desired that head 120 fly above disc 140 at a predetermined rollangle, which is typically zero. The roll angle relates to the angle thathead 120 is rotated about x-axis 142 relative to disc surface 140. Inthe example shown in FIG. 3, the roll angle is approximately zero.Unfortunately, when head 120 is mounted to load beam 148, it isgenerally oriented at an undesired roll angle. The desired roll anglecan be set using a static attitude adjust machine (SAAM). The SAAMincludes clamping members which can twist rigid beam section 156 aboutlongitudinal axis 158 (x-axis 142) to set the roll static angle of head120 to the desired setting (typically zero degrees).

FIG. 4 shows an example of a load beam 148 (without gimbal 150) withclamping members 174 of a SAAM positioned along rigid beam section 156.The details of clamping members 174 and the components the SAAM to whichclamping members 174 attach, are not shown to simplify the illustration.Rigid beam section 156 includes proximal end 176 and distal end 178.Clamping members 174 generally include distal clamping member 180positioned adjacent distal end 178 of rigid beam section 156 and aproximal clamping member 182 positioned toward proximal end 176 of rigidbeam section 156. In general, one of the clamping members 180 or 182 isrotated, relative to the other clamping member, by an adjust anglethereby twisting the portion of rigid beam section 156 positionedtherebetween to the adjust angle. This twisting of rigid beam section156 produces stresses in rigid beam section 156 which, when in excess ofa yield value, causes permanent deformation of rigid beam section 156and results in an adjustment to the roll static angle of head 120.

In the prior art, it was thought to be beneficial to spread out thetwisting of rigid beam section 156 over its entire length to minimizedamage to rigid beam section 156. This was accomplished by positioningdistal and proximal clamping members 180 and 182 as far apart aspossible along rigid beam section 156. This is shown in FIG. 4 whereproximal clamping member 184, as found in the prior art, is positionedadjacent proximal end 176 of rigid beam section while distal clampingmember 180 is positioned as close to distal end 178 as possible, asshown in FIG. 4. The spacing from distal end 178 is due to theattachment of gimbal 150 (FIG. 3). As a result, distal clamping member180 is generally positioned near tooling hole 186.

The distance separating clamping members 180 and 184, as found in theprior art, is defined as distance 188 which is the distance betweeninside edge 190 of clamping member 184 and inside edge 192 of distalclamping member 180. Distance 188 is generally greater than 31% oflength 194 of load beam 148, which is defined as the distance betweencenter 196 of swage hole 162 and dimple 164 of flexure arm 160. Length194 of a load beam 148 of a typical HGA 122, such as those mentionedabove, is 0.6 inches and distance 188 is approximately 0.216 inches. Theprior art positioning of clamping members 184 and 180 maximizes theadjust angle that rigid beam section 156 must be twisted to produce adesired adjustment of the roll static angle of head 120.

Although contrary to the rationale for the method used by the prior art,one aspect of the present invention involves reducing the distancebetween proximal clamping member 182 and distal clamping member 180 toimprove the relationship between a change in the roll static angle ofhead 120 to a change in the adjust angle. The magnitude of the stresseswithin rigid beam section 156 when it is twisted depends, in part, onthe distance separating proximal and distal clamping members 182 and180, respectively. For a given adjust angle, as the distance separatingproximal and distal clamping members 182 and 180 decreases, themagnitude of the stresses within rigid beam section 156 increases. As aresult, the adjust angle required to cause permanent deformation torigid beam section 156 decreases as the distance separating the clampingmembers 180 and 182 decreases. In one embodiment, prior art proximalclamping member 184 is replaced by proximal clamping member 198 which isseparated from distal clamping member 180 by a distance 200 as measuredbetween inside edge 202 of proximal clamping member 198 and inside edge192 of distal clamping member 180. Distance 200 is shorter than distance188 of the prior art. As a result, the relationship between a change inthe roll static angle of head 120 to a change in the adjust angle isimproved. In other words, a load beam 148 twisted with clamping members198 and 180 that are positioned in accordance with the presentinvention, is more sensitive to a change in the adjust angle than wouldotherwise be possible using roll static angle adjustment methods foundin the prior art.

In one embodiment of the invention, distance 200 is preferablyapproximately 21% of length 194 of load beam 148. For example, if islength 194 is 0.6 inches, distance 200 is preferably approximately 0.126inches. Distance 200 is generally limited by the maximum twist per unitlength that rigid beam section 156 is capable of withstanding withoutcausing undesired damage to rigid beam section 156, such as theformation of kinks or other discontinuities. It has been determinedexperimentally that this limit is approximately 4% of length 194 oftypical load beams 148. In a more general embodiment of the invention,distance 200 is less than 30% of length 194. Additional embodimentsinclude lengths 200 which are, less than 25% of length 194, less than20% of length 194, less than 15% of length 194, and less than 10% oflength 194. Further embodiments of the invention include additionallimitations of distance 200 where applicable to the above describedlengths 200. These embodiments include lengths 200 which are greaterthan 4% of length 194, greater than 10% of length 194, greater than 15%of length 194, greater than 20% of length 194, and greater than 25% oflength 194. Still further alternative embodiments of the inventioninclude any possible combination of the above maximum and minimumlimitations of distance 200.

During static roll angle adjustment, maximum stress contours wherepermanent deformation of rigid beam section 156 occurs, predominantlytakes place in a high stress region 204 of rigid beam section 156, whichis located approximately within circle 4 and near distal clamping member180, as shown in FIG. 4. These maximum stress contours are found in highstress region 204 due to a reduced cross-sectional area of rigid beamsection 156. One cause of the reduced cross-sectional area of rigid beamsection 156 is the general tapering of rigid beam section 156 fromproximal end 176 toward distal end 178. Another cause is tooling hole186.

In one embodiment of the invention, high stress region 204 is enhancedby forming apertures 206, which are shown best FIG. 5, which is amagnified view of high stress region 204 shown in FIG. 4 without distalclamping member 180. Apertures 206 are positioned in high stress region204, preferably near tooling hole 186, and cause the stresses in highstress region 204 to become higher than they would be without apertures206 for a given adjust angle. As a result, apertures 206 cause the onsetof plastic deformation of rigid beam section to occur earlier and at asmaller adjust angle than would be possible without apertures 206.Furthermore, apertures 206 can be used to control the locations of rigidbeam section 156 where plastic deformation is desired during roll staticangle adjustment, thereby limiting the area of rigid beam section 156that is damaged or permanently deformed.

Apertures 206 are preferably oval in shape, but can also be formed ofvarious other shapes, such as circular, rectangular, and polygonal, asindicated at 206. Apertures 206 are generally positioned at an angle tocoincide with maximum stress contours that develop during the twistingof rigid beam section 156 and extend away from distal clamping member180 toward the distal and proximal ends 178 and 176, respectively, ofthe rigid beam section 156. In one embodiment, apertures 206 aresymmetrically positioned about longitudinal axis 158. In yet anotherembodiment, apertures 206 are symmetrically positioned about an axis208, which is perpendicular to longitudinal axis 156.

The general method used by the present invention to adjust the rollstatic angle of HGA 122 is illustrated in the flow chart of FIG. 6. Atstep 210, a high stress region 204 is formed in rigid beam section 156proximate distal end 178. As mentioned above, the high stress region canbe formed by the narrowing of rigid beam section 156 toward distal end178, by tooling hole 186, or by the formation of apertures 206. At step212, distal clamping member 180 is coupled proximate distal end 178 andhigh stress region 204 of rigid beam section 156. At step 214, proximalclamping member 198 is coupled to rigid beam section 156 a distance 200away from distal clamping member 180 toward proximal end 176 of rigidbeam section 156. Finally, at step 216, either distal clamping member180 or proximal clamping member 198 is rotated about longitudinal axis158 such that the relative angular position of the distal and proximalclamping members 180 and 198 reaches an adjust angle resulting in achange in the roll static angle of head 120. The distance separatingdistal and proximal clamping members 180 and 198, respectively, is lessthan 30% of length 194 of load beam 148. This method results in animprovement of the relationship between the change in the roll staticangle of head 120 to a change in the adjust angle.

At least three advantages have been realized by the improved method ofthe present invention. One advantage of the present invention is thatload beam 148 becomes more sensitive to the twisting of rigid beamsection 156 by clamping members 180 and 198 as compared to the priorart. For a given adjust angle that rigid beam section 156 is twisted,the method of the present invention results in a greater adjustment tothe roll static angle of head 120 than the method used in the prior art.For example, experiments have shown that rotating the relative angularposition of clamping members 180 and 184 that are separated a distanceof 31% of length 194 of load beam 148 (prior art method) to an adjustangle of 1° results in an adjustment to the roll static angle of head120 of 1.24°, whereas twisting rigid beam section 156 by the same amountusing clamping members 180 and 198 that are positioned in accordancewith the present invention, results in an adjustment to the roll staticangle of head 120 of 1.38°. In other words, a load beam 148 will require11% less twisting of rigid beam section 156 to produce the desired rollstatic angle adjustment at head 120 with the method of the presentinvention as compared to that of the prior art.

Another advantage of the present invention is that the asymmetry of loadbeam 148 is moved toward distal end 178, which reduces the likelihood ofoff-track errors when used in a disc drive 110 (FIG. 1). Load beam 148,as with all mechanical structures, has various resonant modes. When aresonant mode of load beam 148 is excited, load beam 148 will oscillateat the resonant frequency. The resulting movement of load beam 148 canoccur in a bending mode, a twisting mode or a combination of the two.When load beam 148 is symmetric about longitudinal axis 158 (FIG. 2),the first bending mode of load beam 148 will cause load beam 148 tooscillate in a vertical plane or along the y-axis. However, when a twistis made in rigid beam section 156 about the longitudinal axis 158 toadjust the roll static angle, rigid beam section 156 becomes asymmetricabout longitudinal axis 158 thereby introducing a twisting mode. Thetwisting mode of load beam 148 will cause head 120 to oscillatehorizontally or along the z-axis 146 (FIG. 2), which can result inoff-track errors and limit the performance of disc drive 110. Themagnitude of the horizontal oscillations for a given load beam 148depends, in part, on the location of the asymmetry of rigid beam section156 caused by the roll static angle adjustment. In general, the closerthe asymmetry of rigid beam section 156 is to proximal end 176, thegreater the magnitude of the horizontal oscillations that will beproduced at the resonant frequency and, thus, the greater the likelihoodthat off-track errors will occur. By moving proximal clamping member 198closer to distal end 178 of rigid beam section (FIG. 4), the asymmetryof rigid beam section 156 is moved further from proximal end 176 andcloser to distal end 178, as compared to the prior art. As a result, themagnitude of the horizontal oscillations that are produced in load beam148 of the present invention at the resonant frequency are reducethereby reducing the likelihood of off-track errors and improving discdrive performance.

Yet another advantage of the present invention is that the adjustment ofthe roll static angle of head 120 is more accurate since rigid beamsection 156 yields more quickly than would be possible using prior artmethods. The method of the present invention produces higher stresses inrigid beam section 156 due to a shorter free length available fortwisting. These higher stresses cause the yield stress of rigid beamsection 156 to be reached faster thus leading to quicker plasticdeformation of rigid beam section 156. As a result, the sensitivity of achange in the roll static angle to a change in the adjust angle isimproved.

In summary, one aspect of the present invention is directed toward amethod for adjusting a roll static angle of a head 120 of an HGA 122.The HGA 122 includes a load beam 148 having a length 194, a longitudinalaxis 158, and a rigid beam section 156. In one step of the method a highstress region 204 is formed in the rigid beam section 156 proximate adistal end 178. Next, a distal clamping member 180 is coupled to therigid beam section 156 proximate the distal end 178 and the high stressregion 204 and a proximal clamping member 198 is coupled to the rigidbeam section 156 a distance 200 away from the distal clamping member 180toward a proximal end 176. The distance 200 separating the distal andproximal clamping members is less than 30% of the length of the loadbeam. Finally, at least one of the distal and proximal clamping members180 and 198, respectively, is rotated about the longitudinal axis 158such that a relative angular position of the distal and proximalclamping members 198 and 180 reaches an adjust angle resulting in achange in the roll static angle of the head 120. This method results inan improved relationship (sensitivity) between the change in the rollstatic angle to a change in the adjust angle where.

Another aspect of the present invention is directed toward a load beam148 of an HGA 122 for use in a disc drive 110. The load beam 148includes a mounting portion 152, a flexible beam portion 154, a rigidbeam section 156, and a flexure arm 160. The mounting portion 152 isadapted to couple the load beam 148 to a track accessing arm 124 of thedisc drive 110. The flexible beam portion 154 is attached to themounting portion 152 and is adapted to supply a pre-load which isapplied to the head 120 through flexure arm 160. The rigid beam section156 has a proximal end 176 attached to the flexible beam portion 154, adistal end 178 attached to flexure arm 160, a longitudinal axis 158, anda high stress region 204 having plurality of apertures 206. Theapertures 206 define high stress contours of the rigid beam section 156where plastic deformation of the rigid beam section 156 is desiredduring roll static angle adjustment.

It is to be understood that even though numerous characteristics andadvantages of various embodiments of the present invention have been setforth in the foregoing description, together with the details of thestructure and function of various embodiments of the invention, thisdisclosure is illustrative only, and changes may be made in details,especially in matters of structure and arrangements of parts within theprinciples of the present invention to the full extent indicated by thebroad general meaning of the terms in which the pending claims areexpressed.

What is claimed is:
 1. A load beam of an HGA for use in a disc drivecomprising: a mounting portion adapted to couple the load beam to atrack accessing arm of the disc drive; a flexible beam portion attachedto the mounting portion and adapted to supply a pre-load force; aflexure arm adapted to apply the pre-load force to a head; and a rigidbeam section having a proximal end attached to the flexible beamportion, a distal end attached to the flexure arm, a longitudinal axis,a tooling hole located adjacent the distal end, and a high stress regionhaving a plurality of apertures extending in rows from adjacent thetooling hole toward the distal and proximal ends, the rows beingoriented at oblique angles relative to the longitudinal axis anddefining high stress contours of the rigid beam section where plasticdeformation is desired during roll static angle adjustment.
 2. The loadbeam of claim 1, wherein the apertures have shapes selected from a groupconsisting of circular, oval, rectangular, and polygonal.
 3. The loadbeam of claim 1, wherein the apertures are in a pattern that issymmetric about the longitudinal axis.
 4. A load beam of a head gimbalassembly (HGA) for use in a disc drive comprising: a mounting portionadapted to couple the load beam to a track accessing arm of the discdrive; a flexible beam portion attached to the mounting portion andadapted to supply a pre-load force; a flexure arm adapted to apply thepre-load force to a head; and a rigid beam section having a proximal endattached to the flexible beam portion, a distal end attached to theflexure arm, a longitudinal axis, a tooling hole located adjacent thedistal end, and a high stress region having a plurality of aperturesextending in radial rows from the tooling hole, the rows oriented atoblique angles relative to the longitudinal axis and defining highstress contours of the rigid beam section where plastic deformation isdesired during roll static angle adjustment, wherein the apertures arein a pattern that is symmetric about an axis that is perpendicular tothe longitudinal axis.
 5. A load beam of a head gimbal assembly (HGA)for use in a disc drive comprising: a rigid beam section having aproximal end and a tooling hole at a distal end; and an aperture meansfor defining high stress contours of the rigid beam section whereplastic deformation of the rigid beam section is desired during rollstatic angle adjustment, the defined high stress contours extendingradially from adjacent the tooling hole toward the proximal and distalends of the rigid beam section.